WO2005111443A1 - Palier pour arbre d'entrainement intermediaire en particulier d'une transmission d'essieu avant toutes roues motrices - Google Patents

Palier pour arbre d'entrainement intermediaire en particulier d'une transmission d'essieu avant toutes roues motrices Download PDF

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Publication number
WO2005111443A1
WO2005111443A1 PCT/EP2005/005163 EP2005005163W WO2005111443A1 WO 2005111443 A1 WO2005111443 A1 WO 2005111443A1 EP 2005005163 W EP2005005163 W EP 2005005163W WO 2005111443 A1 WO2005111443 A1 WO 2005111443A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
drive pinion
inner ring
drive
pinion shaft
Prior art date
Application number
PCT/EP2005/005163
Other languages
German (de)
English (en)
Inventor
Hartmut Nied
Wolfgang Oetken
Ulrich Scholz
Original Assignee
Daimlerchrysler Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daimlerchrysler Ag filed Critical Daimlerchrysler Ag
Publication of WO2005111443A1 publication Critical patent/WO2005111443A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/56—Systems consisting of a plurality of bearings with rolling friction in which the rolling bodies of one bearing differ in diameter from those of another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/038—Gearboxes for accommodating bevel gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2229/00—Setting preload
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/42—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon
    • F16H2048/423—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon characterised by bearing arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H57/022—Adjustment of gear shafts or bearings
    • F16H2057/0221—Axial adjustment

Definitions

  • the invention relates according to claim 1, a bearing for a drive pinion shaft, in particular an all-wheel front axle transmission.
  • the bearing outer ring of the bearing assigned to the inner shaft end of the drive shaft is supported by an annular housing insert both radially outward and in the direction of the bearing arrangement pointing towards the O arrangement relative to the axle housing.
  • the housing insert which is designed as a component separate from the axle housing and is aligned concentrically with the bearing axis, has an annular flange on its outer circumference.
  • the ring flange and the tapered rollers of the bearing supported by the housing insert are arranged in a region of the bearing axis in such a way that the resultant of the bearing force is introduced into the housing insert in the axial region of the ring flange.
  • the axle housing is made of light metal and that the radial support of the bearing outer ring of the bearing assigned to the outer shaft end takes place directly in a bearing eye of the axle housing and an angle ⁇ that is assigned between the rolling surface of the outer bearing ring and the outer shaft end of the drive shaft Bearing and the bearing axis of the drive shaft is included, a distance L between a first axial support surface of the axle housing for the bearing outer ring of the bearing associated with the outer shaft end of the drive shaft and a second support surface of the axle housing for the ring flange, a thermal expansion coefficient G associated with the material of the axle housing the material of the drive shaft and the use of the associated second coefficient of thermal expansion ⁇ L , a temperature difference ⁇ t G between the temperature of the axle housing, at which the press fit between d em bearing eye of the axle housing and the bearing associated with the outer shaft end of the drive shaft goes to zero and the output temperature and a temperature difference ⁇ t L between the mean temperature of the drive shaft and the bearing associated with the
  • the object of the invention is to provide a bearing of a drive pinion shaft that is precisely adjustable with regard to the bearing preload.
  • a roller bearing in an O arrangement is provided for mounting the drive pinion shaft.
  • This bearing can in particular be a tapered roller bearing.
  • One tapered roller bearing is closer to the pinion head and another tapered roller bearing is closer to a screwable thread carrier with which the preload is introduced into the bearing.
  • the thread carrier is screwed onto the pinion head in the axial direction until it rests so firmly against a shoulder of the drive pinion shaft that further screwing is no longer possible.
  • the two inner bearing rings are thus clamped between the thread carrier and the pinion head, wherein they are supported against one another in the housing in the flow of tension via the outer bearing rings.
  • the bearing preload is therefore specified via the axial adjustment path.
  • This setting path which specifies how far the bearing inner ring remote from the pinion head is displaced onto the bearing inner ring near the pinion head, is specified by means of individually adapted path setting means, which are arranged between the thread carrier and the bearing inner ring closer to it.
  • the individually adjusted path setting means can in particular be spacers or spacer rings.
  • individually adapted material from a shoulder of the drive pinion shaft or the thread carrier or a sleeve between the thread carrier and the bearing inner ring or the bearing inner ring itself can also be ground.
  • the spacer ring or the material take-off can lie directly in the flow of tension from the thread carrier to the bearing inner ring.
  • the spacer ring or the material take-off can be parallel to the latter flow of tension and thereby determine the distance between the thread carrier and the shoulder of the drive pinion shaft, so that the distance of the bearing inner ring at least indirectly from the thread carrier from the drive pinion shaft is also determined.
  • the distance of the bearing inner ring near the pinion head can be predetermined by the fact that it rests on the pinion head.
  • the thread carrier can in particular be an adjusting nut.
  • a connecting flange can be slid axially displaceably and coaxially on the drive pinion shaft between the inner ring of the bearing remote from the pinion head and this adjusting nut.
  • This connecting flange for torque transmission can thus be supported in a particularly advantageous manner, on the one hand, directly or indirectly on the thread carrier and, on the other hand, on the bearing inner ring.
  • the invention is particularly advantageous in combination with such an axially displaceable connecting flange, since a splined shaft connection can be provided for the torque transmission from the connecting flange to the drive pinion shaft. required axial movement, but is subject to strong manufacturing tolerances. As a result of the travel setting according to the invention, the tolerance-related scattering on the spline gears plays no role in the production of the bearing preload, in contrast to the bearing preload settings by means of friction torque measurement.
  • the setting of the bearing preload is particularly precise because the thinnest area of the two bearing inner rings is not clamped between two axial shoulders according to the invention. This thinnest area lies at the axially facing bearing ends of the bearing raceways of the two inner rings. If, contrary to the invention, the bearing inner ring were clamped between an adjusting nut and an axial shoulder and deformed at the thinnest area due to the low material thickness, then a preload setting would be imprecise and not reproducible due to the deformations on the bearing inner ring which are very widely scattered depending on the bearing, depending on the tolerance.
  • the thinner area is the thinner the larger the angle that is spanned between the longitudinal axis of the rolling element and the longitudinal axis of the bearing or the longitudinal axis of the drive pinion shaft.
  • the configuration according to the invention makes it necessary to measure the necessary thickness of the spacer or the material removal on the heel.
  • the provision of a large number of spacers of different thicknesses is advantageous, whereas in medium-sized series use and in the production of individual pieces, the aforementioned material acceptance is also an option.
  • Commercial vehicle production in particular can be seen as a medium-sized series production relative to passenger car production.
  • the required thickness or material can be measured using the "push-pull" method by "pulling” and "pressing”. measure the storage unit in the preloaded condition, the necessary thickness or material decrease can be determined.
  • the required axial dimension of the spacer ring can be determined by the fact that by axially "pulling” and “pressing” the drive pinion shaft with the desired pretensioning force in the preassembled state of the bearing in the gearbox housing, the distance between the bearing inner ring of the roller bearing remote from the pinion and the significant stop measured the drive pinion shaft and from this the axial dimension of the spacer ring is determined.
  • the spacer ring, the bearing inner ring and the hub of the drive flange are placed on the drive pinion shaft and axially clamped against the significant stop or shoulder by tightening the threaded nut with a predetermined torque.
  • the two tapered roller bearings can be preassembled in a particularly advantageous manner with a housing insert as a bearing unit.
  • the two inner rings of the bearing are precisely clamped between two punches or hollow mandrels under the preload that will be necessary later.
  • the bearing unit is then measured in this setting. If a hollow mandrel is used to brace the bearing unit, the sensor can be passed through the hollow mandrel.
  • FIG. 1 shows a partial section through a bearing according to the invention in the first embodiment in a housing plane containing the bearing axis
  • 2 shows a partial section in a housing plane containing the bearing axis through a bearing according to the invention in the second embodiment
  • FIG. 3 shows a partial section in a housing plane containing the bearing axis through a bearing according to the invention in the third embodiment, several components shown in detail in FIG. 1 being summarized to form a housing insert, and
  • FIG. 4 shows a storage unit which can be used in the aforementioned exemplary embodiments.
  • a drive pinion shaft 6 rotates with a drive pinion 34 within a bearing unit about a bearing axis 14-14.
  • the drive pinion shaft 6 is mounted in a bearing bush 100 via two tapered roller bearings 7, 8.
  • the tapered roller bearing 8 forms a pinion flange bearing or a bearing remote from the pinion head.
  • the tapered roller bearing 7 forms a drive pinion bearing or a bearing close to the pinion head.
  • the bearing bush 100 has two radial bearing surfaces and two axial contact surfaces designed as a bearing shoulder.
  • the bearing bush 100 is supported in the radial direction via a mating surface in a gear housing 11 and in a bearing part 101.
  • the bearing bush 100 is via an external thread 102 screwed to the bearing part 101.
  • the bearing part 101 is designed as a bearing cover and has a corresponding internal thread 103.
  • the bearing cover is screwed to the gear housing 11 via a plurality of screw fastenings 35.
  • a separate ring flange 104 is provided which braces the bearing part 101 and the bearing bush 100 by means of the screw fastening 35 against a spacer disk 105 abutting the gear housing 11.
  • the position of the drive pinion 34 relative to the ring gear is determined in the cold temperature state in the axial direction via this spacer 105.
  • a sealing ring 106 designed as an O-ring is provided radially within the spacer 105 between the gear housing 11 and the bearing cover 101.
  • the bearing preload of the bearing unit is set via a spacer ring 32.
  • FIGS. 2 and 3 also correspond to the exemplary embodiment according to FIG. 1 in particular in the following points:
  • the drive pinion shaft 6 is formed in one piece at its one shaft end with the coaxial drive pinion 34, which has a conical external toothing 5. Furthermore, the drive pinion shaft 6 is supported by the roller bearing 7 arranged close to the drive pinion 34 and by the roller bearing 8 arranged remotely from the drive pinion 34 in a gear housing 11, which is only indicated in the drawing, the bearing axis 14-14 and the central axis of the drive pinion shaft 6 coinciding.
  • the roller bearings 7 and 8 are designed as tapered roller bearings, aligned in an O arrangement to one another and with their respective outer race 9 or 10 in a corresponding bearing eye 12 or 13 of a ring-shaped Migen multi-part housing insert 15 - both radially and in the directions of the bearing axis 14-14 axially facing each other - are each essentially rigidly supported.
  • the multi-part housing insert 15 is shown in one piece in the drawing in FIGS. 2 and 3. However, it is also possible in practice to produce this housing insert 15 in one piece.
  • the housing insert 15 has the radially outer ring flange 104, which is fixed to the transmission housing 11 by means of screw fastenings 35 in a manner fixed in terms of movement, but releasably.
  • the drive pinion shaft 6 each has a bearing seat 16 or 17 for the bearing inner rings 18 and 19 of the two rolling bearings 7 and 8 and an axial abutment 20 or 21 for their direct or indirect support on the one bearing inner ring 18 or 19 in the other bearing inner ring 19 or 18 pointing direction of the bearing axis 14-14.
  • the axial abutment 21 of the drive pinion shaft 6 is supported on the associated bearing inner ring 19 of the roller bearing 8 remote from the pinion indirectly via a hub 22 of a drive flange 23, on which one is ultimately driven by a drive motor.
  • Tor drivable drive shaft can be articulated.
  • the hub 22 is arranged concentrically to the drive pinion shaft 6 and connected to the latter by means of spline teeth 27 in a rotationally fixed manner.
  • the propeller shaft can in particular be the side shaft of the front output of an all-wheel drive train.
  • the cardan shaft can also be the cardan shaft of a rear axle drive.
  • the three embodiments of the bearing according to the invention differ in the particular arrangement or axial position of a spacer ring provided concentrically on the drive pinion shaft 6 to secure the bearing preload relative to the roller bearings 7, 8.
  • the drive pinion shaft 6 has a concentric annular shoulder, used as a significant axial stop 31, between the spline toothing 27 for the rotationally fixed engagement of the hub 22 of the drive flange 23 and its threaded end journal 37, the spacer ring 32 in question is inserted directly between the stop 31 and the axial abutment 21 and the hub 22, which overlaps the spacer ring 32 arranged radially to it internally, comes into mutual contact with the abutment 21 and the bearing inner ring 19 when the threaded nut 36 is tightened with its end faces.
  • the flow of the bias is shown in the drawing, which is divided into two parallel flows 98, 99.
  • the spacer ring 32 lies in the river 99 parallel to the river 98.
  • the drive pinion shaft 6 has a concentric annular shoulder, used as a significant stop 26, between the bearing seat 17 for the bearing inner ring 19 and the axial driving teeth 27 of the drive pinion shaft 6, the spacer in question 28 is inserted between the bearing inner ring 19 of the roller bearing 8 remote from the pinion and the hub 22 supported axially on the significant stop 26.
  • the support of the hub 22 on the significant stop 26 also ensures that tightening the threaded nut 36 cannot lead to an increase in the bearing preload beyond the design value - but additionally achieves the advantage that the locking forces on the threaded nut 36 of the rolling bearings 7, 8 - in particular of the bearing inner ring 19 - are switched off, so that no possibly elastic deformation of this bearing inner ring can occur, which could otherwise lead to a disturbing influence on the bearing preload.
  • the drive pinion shaft 6 also has a concentric axial drive toothing 27 of the mounting, which is graduated between the bearing seat 17 for the bearing inner ring 19 and the diameter.
  • the bearing inner ring 19 of the roller bearing 8 remote from the pinion overlaps the spacer ring 30 arranged radially on the inside thereof, the hub 22 axially supported axially on the significant stop 29 via the spacer ring 30 and the bearing inner ring 19 being brought into mutual contact when the threaded nut 36 is tightened ,
  • the indirect support of the hub 22 on the significant stop 29 in turn ensures that tightening the threaded nut 36 cannot lead to an increase in the bearing preload beyond the design value, since the locking forces on the threaded nut 36 from the roller bearings 7, 8 - in particular, however are switched off from the bearing inner ring 19.
  • the two roller bearings 7, 8, which are designed as tapered roller bearings, can in particular be designed as low-friction bearings in all the exemplary embodiments.
  • a low-friction bearing is known per se and is advantageous because of the low friction losses.
  • an angle ⁇ > 19 ° is included between the bearing axis 14-14 and the individual longitudinal axis of the rolling pinion of the pinion flange.
  • an angle ⁇ > 23 ° is included between the bearing axis 14-14 of the individual longitudinal axis of the rolling body of the pinion flange.
  • the determination of the necessary thickness of the spacers for setting the bearing preload can be carried out using the "push-pull" method known per se.
  • the necessary thickness of the spacer 32 or 28 or 30 can be determined by the assembly unit from the two roller bearings 7, 8 and the bearing bush 100 between two stamps 200, 201 or hollow mandrels shown in broken lines in the drawing in FIG the pretension required in the installed state according to FIG. 1 is precisely tensioned.
  • the bearings are measured in this tensioned state.
  • the contact surface for the two said punches 200, 201 of the measuring device form the end faces of the bearing inner rings 9, 10 that are axially outside with respect to the arrangement.
  • the sensor can be carried out through the hollow mandrel.
  • the axle drive shown in the exemplary embodiments can be used in particular as a front axle drive in an all-wheel drive train which is designed in accordance with DE 103 33 947.7-14, DE 103 33 946.9-12 and DE 103 33 945.0-12.
  • the latter applications are to be considered as included in the content of this application.
  • the described embodiments are only exemplary configurations. A combination of the features described for different embodiments is also possible. Further, in particular not described features of the device parts belonging to the invention can be found in the geometries of the device parts shown in the drawings.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

La présente invention concerne un différentiel d'essieu avant d'une chaîne de transmission toutes roues motrices. Selon l'invention, le palier de l'arbre intermédiaire (6) se trouve dans un élément rapporté et est composé de paliers coniques à rouleaux (7, 8) disposés en O, dont la précontrainte est réglée selon une course prédéfinie.
PCT/EP2005/005163 2004-05-14 2005-05-12 Palier pour arbre d'entrainement intermediaire en particulier d'une transmission d'essieu avant toutes roues motrices WO2005111443A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004024003.5 2004-05-14
DE102004024003A DE102004024003A1 (de) 2004-05-14 2004-05-14 Lagerung für eine Antriebsritzelwelle insbesondere eines Allrad-Vorderachsgetriebes

Publications (1)

Publication Number Publication Date
WO2005111443A1 true WO2005111443A1 (fr) 2005-11-24

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PCT/EP2005/005163 WO2005111443A1 (fr) 2004-05-14 2005-05-12 Palier pour arbre d'entrainement intermediaire en particulier d'une transmission d'essieu avant toutes roues motrices

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Country Link
DE (1) DE102004024003A1 (fr)
WO (1) WO2005111443A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010009483A1 (de) * 2010-02-26 2011-09-01 Bayerische Motoren Werke Aktiengesellschaft Verfahren zur Einstellung der Lagervorspannung einer Lageranordnung
WO2013149693A1 (fr) * 2012-04-04 2013-10-10 Sew-Eurodrive Gmbh & Co. Kg Dispositif d'entraînement présentant une première et une deuxième partie de carter
WO2015007359A1 (fr) * 2013-07-16 2015-01-22 Sew-Eurodrive Gmbh & Co. Kg Transmission pourvue d'une première et d'une deuxième parties de carter
DE102014223078A1 (de) 2013-11-14 2015-05-21 Schaeffler Technologies AG & Co. KG Rollenlageranordnung für ein ritzel in einem kraftfahrzeugantriebsstrang
CN111853209A (zh) * 2019-04-30 2020-10-30 弗兰德有限公司 具有预加应力的传动装置壳体壁的传动装置
CN113251131A (zh) * 2021-05-19 2021-08-13 山东华成中德传动设备有限公司 一种工业齿轮箱圆锥滚子轴承的预负荷调整方法

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Publication number Priority date Publication date Assignee Title
DE102007061540A1 (de) * 2007-12-20 2009-06-25 Honsel Ag Lagerbuchse für Achsantriebe
CN116438393A (zh) * 2020-10-20 2023-07-14 索尤若驱动有限及两合公司 具有壳体和轴单元的减速器

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Publication number Priority date Publication date Assignee Title
DE19808566C1 (de) * 1998-02-28 1999-07-15 Daimler Chrysler Ag Lagerung einer Antriebswelle eines Achsgetriebes
DE10004419A1 (de) * 1999-05-27 2000-12-14 Daimler Chrysler Ag Meßvorrichtung für eine angestellte Kegelrollenlagerung und Verfahren zur Herstellung einer angestellten Kegelrollenlagerung
DE19953092A1 (de) * 1999-11-04 2001-06-21 Daimler Chrysler Ag Lageranordnung
DE10043799A1 (de) * 2000-09-06 2002-03-14 Daimler Chrysler Ag Achsgetriebe eines Kraftfahrzeugs
EP1367299A2 (fr) * 2002-05-31 2003-12-03 Dana Corporation Différentiel amélioré dans un véhicule

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19808566C1 (de) * 1998-02-28 1999-07-15 Daimler Chrysler Ag Lagerung einer Antriebswelle eines Achsgetriebes
DE10004419A1 (de) * 1999-05-27 2000-12-14 Daimler Chrysler Ag Meßvorrichtung für eine angestellte Kegelrollenlagerung und Verfahren zur Herstellung einer angestellten Kegelrollenlagerung
DE19953092A1 (de) * 1999-11-04 2001-06-21 Daimler Chrysler Ag Lageranordnung
DE10043799A1 (de) * 2000-09-06 2002-03-14 Daimler Chrysler Ag Achsgetriebe eines Kraftfahrzeugs
EP1367299A2 (fr) * 2002-05-31 2003-12-03 Dana Corporation Différentiel amélioré dans un véhicule

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010009483A1 (de) * 2010-02-26 2011-09-01 Bayerische Motoren Werke Aktiengesellschaft Verfahren zur Einstellung der Lagervorspannung einer Lageranordnung
WO2013149693A1 (fr) * 2012-04-04 2013-10-10 Sew-Eurodrive Gmbh & Co. Kg Dispositif d'entraînement présentant une première et une deuxième partie de carter
CN104246305A (zh) * 2012-04-04 2014-12-24 索尤若驱动有限及两合公司 具有第一和第二壳体件的减速器
US10871216B2 (en) 2012-04-04 2020-12-22 Sew-Eurodrive Gmbh & Co. Kg Gear unit having a first and a second housing part
US11549580B2 (en) 2012-04-04 2023-01-10 Sew-Eurodrive Gmbh & Co. Kg Gear unit having a first and a second housing part
WO2015007359A1 (fr) * 2013-07-16 2015-01-22 Sew-Eurodrive Gmbh & Co. Kg Transmission pourvue d'une première et d'une deuxième parties de carter
US10240669B2 (en) 2013-07-16 2019-03-26 Sew-Eurodrive Gmbh & Co. Kg Gearing having a first and a second housing part
DE102014223078A1 (de) 2013-11-14 2015-05-21 Schaeffler Technologies AG & Co. KG Rollenlageranordnung für ein ritzel in einem kraftfahrzeugantriebsstrang
US9631671B2 (en) 2013-11-14 2017-04-25 Schaeffler Technologies AG & Co., KG Roller bearing assembly for a pinion in a motor vehicle drive train
CN111853209A (zh) * 2019-04-30 2020-10-30 弗兰德有限公司 具有预加应力的传动装置壳体壁的传动装置
CN113251131A (zh) * 2021-05-19 2021-08-13 山东华成中德传动设备有限公司 一种工业齿轮箱圆锥滚子轴承的预负荷调整方法
CN113251131B (zh) * 2021-05-19 2022-05-20 山东华成中德传动设备有限公司 一种工业齿轮箱圆锥滚子轴承的预负荷调整方法

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